Trailer brake system



Nov. 16, 1937. A. FARMER I TRAILER BRAKE SZYSTEM 5 Sheets-Sheet 1 Filed Aug. 20

.Zhven/ar'. Jimdlll'armen Nov. 16, 1937 A. L. .FARMER 9 ,2

TRAILER BRAKE SYSTEM Filed Aug. 20, 1954 5 Sheets-Sheet 2 In vn 1'32". 004 1 -.F0rmer rney Nov. 16, 1937 A. FARMER 2,099,263

TRAILER BRAKE SYSTEM Patented Nov. 16 1937 UNITED STATES,

PATENT OFFICE This invention relates generally to air brake systems for vehicle trains, and it may be-stated as a general object of the invention to provide an improved and simplified air brake system for a vehicle train such as a truck and trailer.

Fluid pressure brake systems for vehicle trains have heretofore been either of the straight air type, in which the brake cylinders are connected through a hand control valve with a source of compressed air, or of the automatic type, in which operation of a hand control valve releases pressure in a control line, thereby operating an automatic valve device to cause compressed air stored in an auxiliary tank on the trailer to be introduced to the brake cylinders. It has generally been considered in the past that .the straight air system was in many points superior to the automatic system for short trains,

as for instance a truck and trailer installation,

for the reason of its greater simplicity, and also for the ease by which application and release of the brakes could be graduated by the operator. Straight air systems, however, do not have the important feature of emergency application of brakes in the event of the trailing vehicle breaking away from the hauling vehicle. It is well known that this emergency application feature is arrinherent characteristic of the automatic system, wherein release of air from the connecting control line, as would occur due to a break in said line, causes the breaks to be instantly applied. Accordingly, it has been usual in the past to utilize a combined straight air and automatic system, straight air braking being relied on for all service stops, and automatic braking being utilized for emergency stops, and also com ing into play automatically in the event of trailer break-away. Obviously, it is not necessary in such systems that the automatic side be adapted for nicely graduated application and release of the brakes, and theautomatic side of such systerns has accordingly not been designed for such use.

It is a primary object of the present invention to provide a vehicle-train air brake system of the socalled automatic type, which is exceptionally simple and eminently practicable for truck and trailer installation, and which "at the same time provides nicely graduated control of braking efiort both in application and release of brakes.

It is a further object of the inventionto provide novel valve devices for the brake systemwhich are simple, trustworthy, and generally improved as regards both design and operation.

- In the preferred form of the braking system there is provided a main air pressure reservoir and a hand control valve on the hauling vehicle, and an auxiliary air pressure reservoir and a remote control valve on the trailing vehicle, and

' the brakes are applied by operating the hand control valve to lower pressure in a connecting control line, which causes the remote control valve to pass air from the auxiliary reservoir to the brake cylinders, in general, in the usual manner. The special hand and remote control valves which are characteristic of the present invention, and the particular nature, of the novel interconnections therebetween, as well as the greatlyimproved braking operation obtainable therewith,

will best be left to be discussed in the bodyof the specification.

The same novel hand and remote control valves as used in my automatic air pressure system outlined above, are also generally adapted for incorporation in an alternative yacuum brake system, the remote. controi'valve needing only a small modification to suit it to such use. The characteristics of my vacuum brake system involving use of these same valve devices will also be more fully discussed hereinafter.

The invention will now .be more fully understood by referring to the following detailed description of present preferred embodiments thereof, reference for this purpose being had to the accompanying drawings, in which:

Fig. 1 indicates diagrammatically my automatic air brake system for a truck and trailer train;

valve;

Fig. 3 is a vertical section taken on line 3-3 of Fig. 2 and showing the valve in neutral position; I

Fig. 4 is a view similar to Fig. 3 but the valve in intake position;

Fig. 5 is a view similar to Fig. 3 but showing the valve in exhaust position;

Fig. 6 is a section taken as indicated by line 66 of Fig. 4;

Fig. 7 is a vertical medial section of the remote control valve, the valve being shown in neutral position;

Fig. 8 is a view showing a portion of the valve 2 is a top plan view of the hand control showing of Fig. 7 and showing the parts in brake applying Fig. 11 is a detail section taken on line of Fig. 8; and

Fig. 12'is a diagrammatic view of my alternative vacuum brake system for a truck and trailer train.

Since the present invention concerns only the trailer brake, the truck brake provisions are omitted from the drawings; it will be obvious, however, that the air compressor on the truck may serve both the trailer and truckbraking systems. The air compressor on the truck is designated at l8, and is shown connected by pipe line H with main air pressure reservoir l2. It is sometimes desirable that the air compressor be operated to supply air at a considerably higher pressure than is suitable for use in the trailer brake system; for instance, air at a maximum pressure of 30 lbs. may be suitable for the trailer brake system, while it may be desirable that the compressor supply air at approximately 100 lbs. pressure for use in the truck brake system. In such event a pressure reducingvalve I3 is placed in line H just ahead of main air pressure reservoir i2, and this reducing valve will be adjusted to supply air at the desired pressure 'to reservoir l2, as will be understood.

From reservoir |2 a brake pressure line H extends to the rear end of the truck, and is coupled at |5 to brake pressure line I6 on the trailer, said line l6 leading to the auxiliary air pressure reservoir H which is mounted on the trailer. A check valve 11a is provided in brake pressure line |6 on the trailer just ahead of reservoir l1, so that the pressure in I! will be held in the event of breakage of the pressure line between the truck and trailer. A control line l8 leads from the main reservoir |2 to hand control valve 28, which is in convenient reach of the operator of the truck, and from valve 28 a pressure control line 2| extends to the rear end of the truck, where it is coupled, as at 22, to a pressure control line 23 on the trailer, this line 23 leading to the remote control valve 25. A pressure line 26 leads from auxiliary reservoir H to the top end 2 of remote control valve 25, and a pressure line 21 leads from reservoir IT to the lower end of said valve 25. Numeral 28 designates a brake cylinder, which is operated by air under pressure supplied to line 29 which leads from the lower end of remote control valve 25.

Hand control valve 28 is shown in detail in Figs. 2 to 6, inclusive. This valve has three positions, one in which air is passed from line |8 straight through to control line 2|, a second in which line I8 is blanked and line 2| is permitted to exhaust through the valve and through a discharge pipe 34 to atmosphere, and a third or neutral position, in which supply line I8 is blanked and at the same time the pressure in control line 2| is held. The valve has a hollow body 35 provided with an integral upper head 36 and a removable valve base 31, the latter being provided with annular flange 38 which engages the lower end of body 35 and is secured thereto by means of screws 39. The valve body is shown provided with a flange 48 through which it may be mounted on any suitable support.

Valve base 31 is provided on one side of center with a through air passage 42 formed at its upper end with a conical valve seat 43 for a downwardly and outwardly seating conical valve 44, this valve being shown provided with a downwardly extending fluted guide stem 45 which fits and slides in passage 42. Valve head 31 is also provided, on the side of center opposite said passage 42, with a through air passage 48 which has formed therein a conical seat 49 for an upwardly and inwardly seating conical valve 58, this valve being provided with an upwardly extending fluted guide stem 5| which fits and slides in air passage bore 48a,-and is adapted to project above the upper surface of base 31 when the valve is seated. Air supply line H! is connected with air passage 48, and a discharge line 34, which opens to atmosphere, is connected with air passage 42, so that lines I 8 and 34 have valve controlled communication with the chamber 52 of the valve body. Valve base 3'! is provided with a third through, .air passage 53,

. to which is connected control line 2|, so that the control line is in constant communication with interior valve chamber 52.

Valve 58 has an upwardly extending stem member 54 of diameter less'than part 5|, having on its upper end a head or flange 56, below which is confined a compression valve spring 51 which bears downwardly on the upper side of a valve abutting or operating plate 58, stem 54' passing freely through an aperture 59 in said plate 58. Valve 44, which is diametrically opposite to valve 50, is provided with an upwardly extending stem 68 which passes freely through anaperture 6| formed in the opposite edge of plate 58, and this stem has on its upper end a head or flange 64, on which is seated the lower end of a compression valve spring 65, the upper end of which engages valve head 36 and is positioned by means of a screw 66 set therein, in the manner indicated.

Plate 58 is formed with a central upwardly extending hub or sleeve portion 18 which surrounds and is vertically slidable on a cylindrical cam member provided on a central rotatable valve operating spindle I2. The lower end of spindle I2 is received and has bearing in a socket or step bearing 13 formed in the upper surface of valve base 31, and the upper end of said spindle extends upwardly through head 36, suitable bearings being provided in said head so that the spindle is free for rotation. Fastened, as by screw 14 and key 14a, on the upper end of spindle 12 is the hub portion 15 of an operating handle 16, this hub portion 15 being conveniently provided with an indicating pointer 11 adapted to point to different operating position designations which may be inscribed on the upper surface of the valve body as in the manner illustrated inFig. 2.

Valve actuating plate 58 is guided for movement along the axis of valve operating spindle by means of a pair of vertical guide pins 8|] fastened to valve base 31 and passing freely through bores 88a in bosses 8| which are formed integrally with plate 58 and its hub portion 18 (Fig. 6). Plate 58,is moved vertically as valve spindle 1-2 is rotated, through themedium of a pair of spiral cam grooves 84 cut in the periphery of spindle section 1| and engaged by follower pins which are carried by and extend inwardly from hub member 18, pin members 85 being formed to fit the spiral cam grooves. It will be evident that rotation of spindle 12 by operation of handle 16 will cause plate member 58 to move vertically on spindle section II by reason of the coaction of cam grooves 84 with follower pins 85.

It will be-seen that in the neutral position of Fig. 3 valve actuating plate 58 is spaced a short distance below the head or flange 64 of valve stem 68 and a short distance above the shoulder interior 61 provided at the juncture'of fluted'valve stem portion 5| with reduced stem member 54 of intake valve 50. Plate 58 thus has a limited range of vertical movement (between flange 64 and shoulder 81) within which valves 44 and 50 are undisturbed thereby and. remain'seated on their valve seats under the influence of their respective valve springs, and this range may be termed the neutral range of the valve. The valve being in the,p'osition of. Fig. 3, operation of handle 16 to rotate valve spindle 12 to the right causes action through cam grooves Y04 and pins 65 tolower valve actuating plate 59 into engagement with valve shoulder 81 to unseat valve 50 against its spring 51, as indicated in Fig. 4; and when handle 16 is operated to rotate spindle 12 to'the left from the described neutral position, valve actuating plate 58 is raised and engages valve stem flange 64 'to' lift valve 44 against its spring 65, as indicated in Fig; 5. It is to be noted that valve actuating plate 59-is positively moved from and returned to the neutral position of Fig. 3

inopening. and closing both of valves 44 and 50.

Thus, in the valve'position of Figs. 2 and 3, herein referred to, as neutral position, both of valves 44 and 50 are closed, and air supply line I0 is therefore blanked'and thepressure in control line 22 is held; in the position of Fig. 4, intake valve 50 is open and air from supply line. I8 is passed through to control line 2|; and in the position of Fig. 5 valve 50 is closed to blank supply line I0, and valve 44 is lifted to permit air from the control line to flow'through the valve body and past valve 44, to discharge through line 34 to atmosphere.

The remote control valve 25 is 'shown'in detail in Figs.'7 to 11, inclusive. This valve 25 embodies a body '90 providing vertical axially alined piston chambers 9| and 92 separated by an intermediate head 93. The body is provided with a removable cap 95, which closes the upper end of chamber 9|, and is secured to the valve body by screws 96, and with a lower valve base 91, which closes the lower end of chamber 92 and is secured to the valve body by screws 90. Upper piston chamber 9| is preferably of greater diameter than lower piston chamber 92, as indicated; for instance, though without intention of limiting the invention to such dimensions, if the interior diameter of upper piston chamber 9| is 3", the interior diameter of lower piston chamber 92 may be 2 Pistons |0I and I02 work within chambers 9| and 92, respectively, and are connected together by a rod I04 which passes through partition 93. A leather packing ring I05 and a packing bushing I06 are placed in partition 93 around rod I04 to prevent leakage of air between chambers 9| and 92. Pistons IM and I 02 are mounted on the reduced and screwthreaded upper and lower extremities I01 and I06, respectively, of rod I04, and are fastened in place by nuts H0. The upper end of lower chamber 9|, above piston I02, is preferably open to atmosphere.

Piston I02 is made up of an upper disc II2, a cup leather I I3 immediately below disc I I2, and a plate 4 adjacent the lower'surface of cup leather II3, nut ||0 holding said parts in assembly. Plate 4 has formed integrally therewith a pair of hollow depending posts||5 (see Fig. 10), which have on their lower ends an integrally formed horizontal valve actuating plate II6.- Vertical guide rods II1'are set in valve base 91 and extend upwardly through the bores of hollow posts 5 to guide valve actuating plate 0 H6 in its vertical movement'with piston I02.

' distance below valve stem Valve base 01 is provided on opposite sides of its Center with through air passages I20 and I2I, passage I20 beingformed with a conical seat I22 for a downwardly and outwardly seating conical valve I23, and passage -|2I being formed with a conical seat I24 for an upwardly and inwardly seating conical valve I25. Valve I23 is provided with a fluted downwardly extending guide stem portion I30, and with an upwardly extending valve stem I3I This valve stem |3I passes freely through an aperture I32 in plate H6 and has on its upper-end a head or flange I33, which provides a seat for the lower end of a compression .valve spring I34, the upper: end'of which seats against the underside of piston I02 and is positioned by a depending lug I35 formedithereon. Valve I25 has an upwardly extending fluted guide stem I40 which fits air passage bore: HI and projects above the upper surface of. v'alve. base 91, and extending upwardly from fluted stem portion I40 is a reduced valve stem 142. This stem I42 passes freely through an aperture I43 in valve actuating plate H6, and has on itsupper end a head or flange I44, below which is confined the upper end of a compression valve spring I45,

the lower end of which bears downwardly on plate II6. It will be evident that in the neutral valve position of Fig. '7, springs I34 and I45 act to hold their respective valves in v closed position.

Air from control line 23 is introduced to the valve body in such a manner as to act constantly on the lower side of upper piston I0 In the present instance this is accomplished by providing anair passage I in valve body partition- 93, one end of which opens through the top side of said partition, and the other end of which opens through the side of the valve, body and is connected at I5I with control line 23. The brake pressure line 21 which leads from auxiliary reservoir I1 is connected at I52 with air passage I2I which is controlled by upwardly seating valve I25. The air passage I20 in valve base 91,which is controlled by downwardly seating valve I23, is connected to a pipe I54 which discharges to atmosphere. -Valve base 91 is provided with a vthird air passage I55 opening to the interior of chamber 92, and connected thereto is pipe line 20 leading to brake cylinder '20. Air pressure from auxiliary reservoir I1 is constantly applied against the upper side of upper piston IOI. In the present instance, a separate pipe-26 leads air from reservoir I1 and is connected at I56 to a threaded port extending through the upper end of valve cap 95. This provision constantly biases the piston to move in a downward direction.

It will be noted thatin the neutral position of Fig. 7, valve actuating plate I I6 is spaced a short flange I33 and a short distance above shoulder I60 provided at the juncture of fluted valve stem portion I40 with reduced valve stem member I42, thus providing a limited range of vertical movement from the piston and valve actuating plate 6 without operatively engaging either flange I33 or shoulder I60. When pistons I0| and I02 lower from the position of Fig. '1, plate 6 finally engages shoulder I60 to unseat valve I25 against its springs;

' and when the pistons rise above the position of When the brakes are in released position, hand 20 is in the position of Fig. 4,

operating valve I over until pointer 11 inhandle 16 being moved dicates off, with valve .50 unseated and valve 44 seated.

Air from reservoir I2 accordingly is free to flow from line l8 through the valve body into control line 2|, 23 and thence through air passage I50 to act on the underside of upper piston IOI. At the same time air from auxiliary reservoir H, which is at the same pressure as the air in reservoir I2, and is therefore at the same pressure as the air which is acting on the underside of piston IN, is introduced by way of line 26 to piston chamber 9| and acts downwardly on the upper side of piston IOI. lower sides of piston IOI are thus equal, except for the slight differential due to the cross-sectional area of rod I04, and the pair of. pistons I I I02 accordingly take a neutral position which is determined by valve springs I34 and I45, it being evident that said springs act in opposite directions on the piston assembly and accordingly tend to move the pistons to a position in which spring I45 plus thedownward pressure differential on the piston due to rod I04 is balanced by spring I34. This position is the neutral position of Fig. 7, with valve actuating plate H6 about midway between flange I32 and shoulder I60. The valve I25 which controls admission of air under pressure from auxiliary reservoir l! is at this time being held closed by springs H45, and it will be evident that the air pressure against the lower side of said valve also tends to hold it up against its seat. Valve I23 is at the same time held seated under the influence of its spring I 34.

When it is desired to apply the brakes, handle I6 of hand valve 20 is moved through neutral,

which closes valve 50 and so cuts oil? the supply" of pressure air, and is then moved momentarily to on position, thus opening valve 44 and permitting a quantity of air from the control line to discharge through the valve body and pipe 34 to atmosphere. For instance, assuming normal pressure of 30 lbs. in the main and auxiliary reservoirs, and therefore on both sides of piston IN and in the control line, handle I6 may be held in the last described position just long enough, say, to allow a reduction of 10 lbs. in the pressure in the control line and below piston IOI, after which handle 16 may be returned to neutral. In this position (neutral), valves 44 and50 are both closed, so that a pressure of 20 lbs. will be held below piston II. The reduction of pressure below piston IOI then causes said piston to descend, moving lower piston I02 and valve actuating plate 6 downwardly until plate I6 engages valve stem shoulder I60 and unseats valve I25 (Fig. 8), and so permits fiow of air from auxiliary reservoir I! through line 21 into lower piston chamber 92, and thence out through passage I56 and line 29 to the brake cylinders.

This flow of air continues until the air pressure so let into chamber 32 acts upwardly on the lower side of piston I02 with a force which is sufficient just to overcome the differential on upper piston I0l created by the drop in pressure below it, at which time pistons lol and I02 move upwardly and so allow valve I25 to close. In this upward movement the pistons do not rise on up to the position of Fig. 9, since the overbalancing force below piston I02 which is causing the pistons to rise is not great, valve I 25 closing before substantial excess force is developed; the upward movement of the pistons is therefore arrested by compression of valve spring I45 before plate IIG reaches valve stem flange I33.

Thus by virtue of the lowering of pistons IN The pressures on the upper and and I02 and the opening of valve I25, air from the auxiliary pressure tank flowed through the valve body and into the brake cylinder, building up a certain pressure therein and causing the brakes to be applied with a certain force depending upon the length of time valve operating handle I6 was held in on position, and therefore upon the amount by which the pressure in the control line and below piston IOI was reduced.

A further operation of. valve handle 16 to still further depress the pressure in the control line will then cause another lowering of remote control valve pistons WI and I02, and therefore a further opening of valve I25 to increase the pressure in the brake cylinders, followed by another return-upward movement of pistons WI and I02 when valve handle I6 is returned to neutral position and the pressure below piston I02 again overcomes the downward force on piston due to the difierential of pressures thereon. Thus the pressure in the brake cylinders may be built up by successive operations of valve control handle I6 between on position and neutral, and so may be built up gradually. until the desired braking effort is obtained. With achievement of skill by the operator, he will not, however, ordinarily increase the braking effort by a succession ofv operations of the valve handle, but will at once by a single operation of the valve handle build up the pressure in the brake cylinders to cause a relatively heavy application of the brakes, and

i may then reduce the pressure in the brake cylinders as speed is reduced, in the manner hereinafter to be explained.

When an emergency stop is to be made, valve .handle 16 is moved over to on position and left there, so as to exhaust all of the pressure air from the control line and reduce the-pressure below piston IM to atmosphere pressure. This of course causes pistons IM and I02 to descend and open valve I25, as before. Now it will be observed that with pistons IM and I02 in this lowermost position (Fig. 8), the force tending to raise the pistons is the pressure of the air let in through valve I25 and acting on the bottom of piston I02, plus the upward force exerted on the piston by the compressed valve spring I34. And if piston I02 were of the same area as piston N, e D tons would tend to rise before the full pressure available from pressure reservoir I! had built up in the brake cylinder, since air at the maximum pressure acting downwardly on piston IOI would be equalized" and overcome by air at somewhat less pressure acting upwardly on piston I02 plus the upward force exerted on piston I02 by spring I 34. Consequently, so that the pistons will not rise until the maximum pressure available has built up below piston I02, piston I02 is made f reduced area, such that the total upward force on said piston, including the force exerted by spring I34, will not overcome the downward force on piston I0| until the full pressure available has been built upin the brake cylinder. By making piston I 02 sufliciently small, and choosing a spring I 34 of proper strength, it is possible to maintain the pistons down in the brake applying position of Fig. 8 when the control linev pressure is completely exhausted, such a condition obtaining when the upward force on piston I02 due to the compression of spring I34 plus the upward force due to the maximum air pressure on the underside of piston I 02 is not sufficient to overcome the downward force of the pressure air on the top side of piston IOI. In such an instance valve I25 is held open and the pressure from auxiliary tank II'is' maintainedin continual communication with thejbrake cylinder. This last is the preferred form 01 the system. 3

When the brakes are to be released, the pressure in the brake cylinder is exhausted by moving hand control valve I6 over to off position, valve 20 then being in the position of Fig. 4, with exhaust valve 44 closed and intake valve 50 open. Air under pressure from main reservoir I2 then flows through valve 20 into control line 2I, 23,

' and builds up the pressure below remote control valve piston IOI. Assuming now that the valve handle is left in off position sufficiently lon to build the pressure below piston IOI back up to .the same maximum pressure as the air which is acting downwardly on piston IN, the pressures on the two sides of said pistons will be substantially balanced (except of course for the small difierential due to the area of rod I04), and the pressure of the air below piston I02, which is the same as the pressure in the brake cylinder, will move the pistons .to the extreme upper release position illustrated in Fig. 9, the upward force on the pistons under such circumstances being sufficient to cause compression of valve spring I45. In moving to this latter position, valve actuating plate I I6 engages flange I33 on the stem of valve I23 and lifts and unseats said valve against its spring I34. The air in the brake cylinder then discharges through line 29, valve chamber 92, and line I54 to atmosphere. This exhaustion of air from the brake cylinder continues until the pressure below piston I02 has been reduced substantially to atmospheric pressure, when Valve spring I45 acts to move the piston back down to the neutral position of Fig. 7. The brake system is then back to its original condition, valves I23 1 and I25 both being closed.

It is also possible to effect a gradual release of the brakes by moving valve handle '10 momen-' tarily to "off" position and then back to neutral,

so thatat'first the pressure below piston IN is built up say just a few pounds above atmospheric. The resulting increase in upward force on the pistons is then suiiicient to move them upwardly momentarily to the release position of Fig. 9, in

which air begins to discharge from the brake cylinders past valve I23, which is then unseated. The immediately resulting reduction of pressure below piston I 02 then decreases the upward force on the pistons, and when the resultant upward component of force on the pistons due to-pr'essure of air then falls below ,the value necessary to hold them in their uppermost release position against the force of valve spring I", the pistons move back down to the neutral position of Fig. 7, only a part of the pressure in the brake cylinder having been released. It will thus be obvious that by a succession of operations of valve handle 16 between off position and neutral the pressure in the brake cylinders can be very gradually released. I From what has now been said it will'be evident creasing the pressure in the control line. I accordingly provide a three-way pet-cock I'I0-in the line 29 between the remote control valve and the brake cylinder, this pet-cock normally allow.- ing the air to flow through line 29, but being adapted to be operated to discharge the air which is being held in the brake cylinder to atmosphere.

Attention is directed to the fact that the pis-' tons have a definite range of travel between the points at which the intake and exhaust valves are opened. Thisv provision is of importance as it permits piston I02 to return to neutral or intermediateposition from its air admitting position at the lower end of its chamber, for instance, without over-traveling and opening the exhaust valve. 'Likewise, this intermediate neutral range permits the pistonlto descend from its upper air-exhausting position without overtraveling and opening the air intake port.

In Fig. 12 I show my vacuum type brake system, which embodies the same valve devices uti-. lized in my previously described pressure brake system. In Fig. 12, numeral 200 designates the vacuum tank on. the truckor hauling vehicle, said tank being exhausted through line 20I which communicates with the intake manifold 202 of the hauling vehicle engine, line 20I being provided with check valve 203. Numeral 205 designates the hand control valve, which may be exactly the same as hand control valve 20 of the air pressure system previously described. For convenience, reference numerals applied to valve 205 are the same as those applied to valve 20, but with primes annexed. 206 is a line leading from vacuum tank 200 to the air port of valve 205 which is controlled by'outwardly seating conical valve 44'.

The port of valve 205 which is controlled by inwardly seating conical valve 50' has connected thereto. an exhaust pipe 201 discharging to atmosphere. The through port 53' of valve 205 has connected thereto a control line 2I0, which is coupled at 2 to control line 2 on the trailing vehicle, this control line 2I2" opening into the upper end of the upper chamber of remote control valve 2. Valve 2 is substantially the same as remote control valve 25 of the previously described air pressure brake system, and for convenience members of valve 2 corresponding to similar members of valve 25 will be given the same reference numerals but with primes annexed. The only difference between remote control valve 25"of the system of Fig. 1 and remote control valve 2 shown in the system of Fig. 12 is the addition in valve 2 of compression spring 2I5 surrounding piston-rod I04 and acting between partition 93 and the underside of upper piston IOI'.

Numeral 2I8 designates vacuum line leading from main vacuum tank 200 and coupled at 2I9 to vacuum line 220 on the trailer, said vacuum line 220 leading to auxiliary vacuum tank '22I mounted on the trailer. A branch line 222 leading from vacuum line 220 connects with air passage I50 which opens into the upper piston chamber below piston IIII.

port in said valve which is controlled by in-' A check valve 223 is provided between the juncture of line 220 and wardly seating conical valve I25 has connected thereto an exhaust pipe 226 which discharges to atmosphere. Connected to the air passage I55 which opens into the lower chamber of valve 2 I4 is a line 230 which leads to brake cylinder 23I.

The brakes are in release position when the valves are in the position indicated in Fig. 12, conical valve 44 of hand control valve 205 being seated and conical valve 50 of said valve being unseated,.and pistons IN and I02 of remote control valve 2" being in their lowermost positions, with conical valve I25',held unseated. The usual pressure depression within manifold 202 exhausts the air from main and auxiliary tanks 200 and 22I, check valves 203 and 223 maintaining the vacuum produced in said tanks. The

same reduced pressure exists below remote control valve piston IllI' due to exhaustion through pipe 222. The outer surfaces of pistons IN and I02 are exposed to air at atmosphere pressure.

To apply the brakes, valve operating handle I6 is operated to seat valve 50' and to unseat valve 44, which has the effect of reducing the pressure in remote control valve 2 I4 above piston IOI' to a value below atmospheric, the air passing by way of control line 2I2, 2I0 and the inner chamber of valve 205 to line 206 and main vacuum tank 200. The resulting reduction of pressure above piston IOI allows pistons WI and I02 to rise under the upward force exerted by spring 2I5, and inso doing allows valve I25 to close and then acts to open valve I23 as the uppermost piston position is reached. In such position air flows from the brake cylinder 23I through line 230 to the lower chamber of the remote control valve, and'then past unseated valve I23 into line 225 to auxiliary vacuum tank 22 I. Pressure within the brake cylinder 23I thus being reduced, brake cylinder piston 23Ia. is moved to apply braking effort.

This ilow of. air from brake cylinder 23I to auxiliary vacuum tank 22I causes a reduction of pressure in the lower chamber of remote control valve 2I4-below piston I02, and when the upward force on piston I02 has thereby been sufliciently reduced, pistons I M and I02 will descend to a neutral or intermediate position, with both valves I23 and I25 closed. In such a position the vacuum produced in the brake cylinder is held at a constant value. A further reduction of pressure above IOI by operation of hand valve control handle I6 to unseat vacuum control valve 44' will then cause a further rise of pistons IOI and I02 to efiect another unseating of conical valve I23 and therefore a further reduction of pressure in brake cylinder 23I and a stronger application of the brakes.

When it is desired to release the brakes, hand valve operating handle I6 is moved to unseat conical valve 50', whereupon atmospheric air flows in through line 201 and builds the pressure in control line 2 I0, 2 I2 and the upper side of the upper chamber of' remote control valve 2M back up to atmospheric pressure, whereupon pistons IOI and I02 descend to the release posl tion illustrated in Fig. 12, with valve I25 .unseated. In the latter position air flows in through pipe 226 and passes by way of line 230 to build the pressure in brake cylinder 230 back -up 'to atmospheric, thus allowing piston 23 Ia to retract to release the brakes.

While I have shown and described present preferred forms of my invention, such disclosure is intended to be illustrative rather than limitative upon the broader claims appended hereto, for various changes in construction and arrangement may be made without departing from the spirit and scope of my invention and or the appended claims.

I claim:

1. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separated by an intermediate partition, a pair of mechanically interconnected pistons, one working in each of said chambers, there being an intake port, an exhaust port, and a brake chamber port in the valve body communicating with the outer end of one of the piston chambers, and an air port communicating with the inner portion of the other piston chamber through which the pressure on the inner side of the piston in said chamber can be controlled, means for maintaining a pressure on the opposite side of said piston, a pair of spring-closed valves controlling the intake and exhaust ports, and valve operating means moving with that piston which is in the valved piston chamber adapted to release both said valves to be closed by their respective springs throughout a limited extent of travel of said piston near the central portion of its stroke, to open the inlet port valve as. the piston moves to the outer end of its stroke and to open the exhaust port valve as the piston moves to the inner end of its stroke.

2. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separated by an intermediate partition, a pair of mechanically interconnected pistons, one working in each of said chambers, yielding means acting in both directions on said pistons to tend to move them toward normal intermediate position 'in their respective chambers, there being an intake port, an exhaust port, and a brake chamber port in the valve body communicating with the outer end of one of the piston chambers, and an air port communicating with the inner portion of the other piston chamber through which the pressure on the inner side of the piston in said chamber can be controlled, means for maintaining apressure on the opposite side of said piston, a pair of normally closed valves controlling the intake and exhaust ports, and means moving with that piston which is in the valved piston chamber adapted to release and allow both said valves to close throughout a given extent of travel of said piston in the vicinity of said normal position, to open the intake port valve as said piston moves to the outer end of its stroke and to open the exhaust port valve as the piston moves to the inner end of its stroke.

3. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separated by an intermediate partition, a pair of mechanically interconnected pistons, one working in each of said chambers, there being a pair of air ports in the valve .body at the outer end of one of said chambers,

an outwardly seating valve controlling one of said air ports, an inwardly seating valve controlling the other of said air ports, a pair of compression springs in said last mentioned chamber acting to hold said valves normally closed, one of said springs being arranged to act on the pistons to tend to move them in one direction in their chambers, and the other of the springs being arranged to act on the pistons to tend to move them in the other direction in their chambers, whereby said pistons are urged to move toward an intermediate neutral position, valve opin the valved piston chamber adapted to release and allow both said valves to close throughout a given neutral range of travel of said piston in the vicinity of saidintermediate position, to unseat the inwardly seating valve when that pis-- ton has travelled past the outer limit of said neutral range in movement toward the outer end of its stroke and to unseat the outwardly seating valve when that piston has travelled past the inner limit of said neutral range in movement toward the inner end of its stroke, and there being a brake chamber port in the valve body opening into the outer end of the valved piston chamber, a control air port communicating with the inner end portion of the other pistonchamher, and means for applying a pressure on the outer side of the piston in the last mentioned 'piston chamber,

4. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separatedby an intermediate partition, one of said chambers being of larger diameter than the other, a pair of mechanically interconnected pistons, one working. in each of said chambers, there being an air port opening into the larger diameter piston chamber through which the pressure on the inner surface of the piston in said chamber can be controlled, and an air port opening into the outer portion of said chamber through which pressure may be applied to the outer side of said piston, and there bein a pair of air ports in the valve body at the outer v end of the other piston chamber, an' outwardly seating valve controlling one of said air ports,

' an inwardly seating valve controlling the other of said air ports, a pair of compression springs in said last mentioned chamber acting to hold said valves normally closed, one oisaid springs being arranged to'act on the pistons intend 'to. move them in one direction'in their chambers,

and the other of the springs being arranged to.

act on the pistons to tend to move them in the other direction in their chambers, whereby said pistons are urged to move toward an intermediate neutral position, valve operating means moving with that piston which is in the valved piston chamber adapted to release and allow both said valves to close throughout a given neutral range of travel of said piston in the vicinity oi.

- said intermediate position, to unseat the inwardly seating valve when that piston has travelled past the outer limit of said neutral range in movement toward the outer end of its stroke. and to piston has travelled past the inper' limit or unseat the outwardly seating valve when that id neutral range in movement toward the inner d of its stroke, and there being a brake cha er port in the valve body opening into the outer end of the valved piston chamber. f

5. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separated by an intermediate partition, a pair oi. mechanically interconnected pistons, one working in each of said chambers,

there being an intake port and an exhaust portin the valve body at the outer end of one of said chambers, an outwardly seating exhaust valve controlling the exhaust port, an inwardly seating intake valve controlling the intake port, a compression spring acting outwardly on the outwardly seating exhaust valve andinwardly on the piston in the valved piston chamber, a com pression spring acting inwardly on the inwardly valve against its spring when saidpiston has travelled past theouter limit of said neutral range in movement toward the outer end of its stroke and'to unseat the exhaust valve against its spring when said piston has travelled past the outer limit of said neutral range in movement toward the inner end oi! its stroke, and there being a brake chamber port in the valve body opening into the outer end of the valved piston chamber. a control air port communicating with the inner end portion-oi the other piston chamber, and means through which a pressure may be appliedon the outer side of the piston in the last mentioned piston chamber.

6. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separated by an intermediate partition, one of said chambers being of larger diameter than the other, a pair of mechanically interconnected pistons, one working in each of said chambers, there being an air port opening into the larger diameter piston chamber through which the pressure on the inner surface 'of the piston in said chamber can be controlled, and an air port opening into the outer portion oi! said chamber through which pressure may be applied to the outer side of said piston, there being an intake port and an exhaust port in the valve body at the outer end of the other piston chamber, an outwardly seating exhaust valve controlling the exhaust port, an inwardly seating intake valve controlling the intake port, a compression spring acting outwardly on the outwardly seating exhaust valve and inwardly on the piston in the valved piston chamber, 'a compression spring acting inwardly on the inwardly seating intake valve and outwardly on the piston in the valved piston chamber, whereby said pistons are urged to move toward an intermediate neutral position in which both said valves are held seated by said springs, and valve actuating means moving'with the piston in the valved pisthere being a brake chamber port in the valve body opening into the outer end of the valved piston chamber.

'7. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separated by an intermediate partition, a pair of mechanically interconnected pistons, one working in each of said chambers, there being an intake port and an exhaust port in the valve body at the outer end of one .of said chambers, an outwardly seating exhaust valve controlling the exhaust port, an'inwardly seatvalve actuating abutment on the piston in the valved piston 1 chamber spaced outwardly from the outer end of said piston, acompression spring acting outwardly on the stem of the exhaust 'valve and inwardly on the abutment carrying piston, a compression spring acting inwardly on the stem of the intake valve and outwardly on said valve actuating abutment, said intake valve stem having a shoulder adapted to be engaged by said abutment to unseat the intake valve when the abutment carrying piston moves to the outer end of its stroke, said exhaust valve stem having a shoulder adapted to be engaged by said abutment to unseat the exhaust valve when said piston moves to the'inner end of its stroke, and there being a brake chamber port in the valve body opening into the outer end of the valved piston chamber.

8. A remote control valvefor a fluid pressure brake system, comprising a valvebody having piston, chambers separated by an intermediate partition, a pair of mechanically interconnected pistons, one workingin each of said chambers, there being an intake port and an exhaust port in the valve body at the outer'end of one of said chambers, an outwardlyseating exhaust valve controlling the exhaust port, an inwardly seating intake valve controlling the intake port, inwardly extending valve stems on said valves, a valve actuating abutment on the piston in the valved piston chamber spaced outwardly from the outer end of said piston, a flange on each of said valve stems near theinner ends thereof, a compression spring encircling the intake valve stem and acting inwardly against the flange on said stem and outwardly against the valve-actuating abutment, a compression spring acting outwardly on the exhaust valve stem flange and inwardly on the pistonin the adjacent piston,

' said intake valve stem having a shoulder adapted valve stem having a shoulder adapted to be engaged-by said abutment to unseat the exhaust valve when said piston moves to the inner end of its, stroke, and there being a brake chamber port in the valve body opening into the outer end of the valved piston chamber.

9. In a fluid trailer brake system, the combination with a main air pressure reservoir and a hand control valve on a leading vehicle, and an auxiliary air pressure reservoir and a brake chamber on a trailer, said auxiliary pressure tank being connected with the main pressure reservoir, and said hand control valve controlling pressure in a' control line leading-from said main reservoir, of a remote control valve adapted to be mounted on the trailer, said remote control valve comprising a valve body having two piston chambers, a pair of mechanically interconnected pistons, one working in each of said piston chambers, said control pressure lineleading from the hand control valve being connected to the remote control valve to introduce air to one of said piston chambers to act on the inner surface of the piston therein, means for applying a pressure against-the outer surface of said piston, there being an intake-port, an exhaust port, and a brake chamber port opening into the outer end of the other of the piston chambers, normally seated valves controlling said intake and exhaust ports, yielding means tending to 'hold said pistons in a normal intermediate position in their respective chambers, means for' opening the valve in the intake port when the piston in the corresponding chamber moves from said intermediate position to the outer end of its stroke, and for opening the valve in the exhaust port when said piston moves from its intermediate position to the inner end of its stroke, a pressure line between said brake chamber port and the brake chamber, and a pressure line between said auxiliary pressure tank and said intake port.

10. In a fluid trailer brake system, the combination with a main air pressure reservoir and a hand control valve on a leading vehicle, and an auxiliary air pressure reservoir and a brake chamber on a trailer, said auxiliary pressure tank being connected with the main pressure reservoir, and said hand control valve controlling pressure in a control line leading from said main reservoir, of a remote control valve adapted to be mounted on the trailer, said remote control valve comprising a valve body having two piston chambers, a pair of mechanically interconnected pistons, one working in each of said piston chambers, said control pressure line leading from the hand control valve being connected to the remote control valve to introduce air to one of said piston chambers to act on the inner surface of the piston therein, means for applying a pressure against the outer surface of said piston, there being an intake port, an exhaust port, and a brake chamber port opening into the outer end of the other of the piston chambers, an inwardly seating valve controlling the intake port and an outwardly seating valve controlling the exhaust port, a compression spring acting-to hold the intake valve closed and to move the piston in the same chamber toward the outer end of its stroke, a compression spring acting to hold the exhaust valve closed and to move said piston toward the inner endof its stroke, whereby the pistons are yieldingly urged by said springs tostand normally in an intermediate position, means moving with the pistons adapted to open the intake valve as the piston in the same chamber moves to the outer end of its stroke, and to open the exhaust valve as said piston moves to the inner end of its stroke, a pressure line between the auxiliary reservoir and saidintake port, and a pressure line between said brake chamber port and the brake chamber.

11. In a fluid trailer brake system, the combination with a main air pressure reservoir and a hand control valve on a leading vehicle, and an auxiliary air pressure reservoir and a brake cham ber on a trailer, said auxiliary pressure tank being connected with the main pressure reservoir, and said hand control valve controlling pressure in a control line leading from said main reservoir, of a remote control valve adapted to be mounted on the trailer, said remote control valve comprising a valve body having two piston chambers, one of larger diameter than the other, a pair of mechanically interconnected pistons, one working in each of said piston chambers, said control pressure line leading from the hand control valve being connected to the remote control valve to introduce air to the larger of said piston chambers to act on the inner, surface of the piston therein, means for applying a pressure against the outer surface of said piston, there being an intake port, an-exhaust port, and a brake chamber port opening into the outer end of the other or the piston chambers,- normally seated valves controlling said intake and exhaust ports, yield- 7 means tending to move said pistons to an intermediate position in their respective chambers, means-for opening the valve in the intake port when the piston in the corresponding chamber moves from 'said intermediate position to the outer end of its stroke, and for opening the valve in the exhaust port when said piston moves from its intermediate position to the inner end of its stroke, a pressure line between said brake chamber port and the brake chamber, and. a pressure line'between'said auxiliary pressure tank and said intake port.

12. In a fluid trailer brake system, the com bination with a main air pressure reservoir and a hand control valve ona leading vehicle, and an auxiliary air pressure reservoir and a. brake chamber on a trailer, said auxiliary. pressure tank being connected with the main pressure reservoir, and said hand control valve controlling pressure in a control line leading from saidrnain reservoir, of a remote control valve adapted to be mounted on the trailer, said remote control valve comprising a valve body having two piston chambers, one of larger diameter than the other, a pair of mechanically interconnected pistons, one working in each of said piston cham-. bers, said control. pressure line leading from i the hand control valve' being connected to. the remote control valve to introduce air to the large er of said piston chambers to act on the inner surface of the piston therein, means for applying a pressure against the outer surface of said piston, there being an intake port, an exhaust port, and a brake chamber port opening into the outer end of the other of the piston chambers, an inwardly seating valve controlling the intake port and an. outwardly seating valve controlling the exhaust port, a compression spring acting to hold theintake valve closed and to press on the piston in the same chamber in the direction of the outer end of its stroke, a compression spring acting to hold the exhaust valve closedand to press on said'piston in the direction of the inner end of its stroke, means moving with the pistons adapted to open the intakevalve as the piston in the same chamber moves to the outer end of its stroke, and to open the exhaust valve as said piston moves to the inner end of its stroke, a pressure line between the auxiliary reservoir and said intake port, and a pressure line between said brake chamber port and the brake chamber. 13. In a fluid trailer brake system, the combination with a main air pressure reservoir and a hand control valve on a leading vehicle, and an auxiliary air pressure reservoir and a brake chamber on a trailer, said auxiliary pressure tank being connected with the main pressure reservoir, and said hand control valve controlling pressure in a control line leading from said main reservoir, or a remote control valve adapted to be mounted on the trailer, said remote control valve comprising a valve body having two piston chambers, a pair of mechanically interconnected pis-- tons, one working in each of said chambers. said control pressure line leading from the hand conr ,trol valve being connected tothe remote control valve to inizroduce air to one of said piston chambars to as on the inner surface of the piston therein, a pressure conduit arranged to introduce air under reservoir pressure to'the valve body tov act against the outer surface, of said piston, there being an intake port, an exhaust port, and a brake chamber port opening into the outer end of the other of the piston chambers, normalis seated valves controlling said intake and exhaust ports, yielding means tending to move said pistons to an intermediate position in their re-' spective chamberameans for opening the valve in the intake port when the piston in the corresponding chamber moves from said intermediate position to the outer end of its stroke, and for opening the valve in the exhaust port when said piston moves from its intermediate position to the inner end of its stroke, a pressure line between said brake chamber port and the brake chamber, and a pressure line between said auxiliary pressure tank and said intake port.

14. In a fluid tr'ailer brake-system, the combination with a main air pressure reservoir and a hand control valve on a leading vehicle, and an auxiliary air pressure reservoir and brake chamber on a trailer, said auxiliary pressure tank being connected with the main pressure reservoir, 3

and said hand control valve controlling pressure in a control line leading from said main reservoir, of a remote control valve adapted to be mounted on the trailer, said remote control valve comprising a valve body having two piston chambers, a pair of mechanically interconnected piston, there being an intake port, an exhaust port, and a brake chamber port opening into the outer end of the other of the piston chambers, an inwardly seating valve controlling the intake port and an outwardly seating valve controlling the exhaust port, a compression spring acting to hold the intake valve closed and to press on the piston in the same chamber in the direction oi the outer end of its stroke, a compression spring acting to hold the exhaust valve closed and to press on said piston in the direction of the inner, end of its stroke, means moving with the pistons adapted to open the intake valve as the piston in,the. same chamber moves to the outer end of its stroke, and to open the exhaust valve as said piston moves to the inner end of its stroke, a pressure line between the auxiliary reservoir and said intake port, and a pressure line between said brake chamber port and the brake I onthe trailer, said remote control valve comprising a valve'body having two piston chambers, one: of larger diameter than the other. a pair of mechanically interconnected pistons, one working in each of said piston chambers, said control pressure line leading from the hand control valve being connected to the remote control valve to introduce air to the larger of said piston chambersto act on the inner,surface of the piston therein, a pressure conduit arranged to introduce air under reservoirpressure to the valve bodyto act against the outer surface of said piston, there being an intake port, an exhaust port, and a brake chamber port opening into the other or the outer end of the piston chambers, normally seated valves controlling said intake and exhausts ports, yielding means tending to move said pistons to an intermediate position in their respective chambers, means for opening the valve in the intake port when the piston in .the corresponding chamber moves from said intermediate position to the outer end of its stroke, and for opening the valve in the exhaust port when said piston moves from its intermediate position to the inner end of its stroke, a pressure line between said brake chamber port and the brake chamber, and

a. pressure line between said auxiliary pressure tank and said intake port.

16. In a fluid trailer brake system, the combination with a main air pressure reservoir and a hand control valve on a leading vehicle, and an auxiliary air pressure reservoir and a brake chamber on a trailer, said auxiliary pressure tank being connected with the main pressure reservoir, and said hand control valve controlling pressure in a control lineleading from said main reservoir, of a remote control valve adapted to be mounted on the trailer, said remote control valve comprising a valve body having two piston chambers, one of larger diameter than the other, a pair of mechanically interconnected pistons, one working in each of said piston chambers, said control pressure line leading from the hand control valve being connected to the remote control valve to introduce'air to the larger of said piston chambers to act on the inner surface of the piston therein, a pressure conduit arranged to introduce air under reservoir pressure to the valve body to act against the outer surface of said piston, there being an intake port, an exhaust port, and a brake chamber port opening into the outer end of the other of the piston chambers, an inwardly seating valve controlling the intake port and an outwardly seating valve controlling the exhaust port, a compression spring acting to hold the intake valve closed and to press the piston in the same chamber in the direction of the outer end of its stroke, a compression spring acting to hold the exhaust valve closed and to press on said piston in the direction of the inner end of its stroke, means moving with the pistons adapted to open the intake -valve as the piston in the same chamber moves to the outer end 01 its stroke, and to open the exhaust valve as said piston moves to the inner end of its stroke, a pressure line between the auxiliary reservoir and said intake port, and a-pressure line between said brake 'chamberport and the brake chamber.

17. A remote control valve for a fluid pressure brake system, comprisirTg a valvebodyhaving piston chambers separated by' an intermediate partition, a pair of mechanically interconnected pistons, one working in each'ofsaid chambers, means for applying a pressure on'the outer end of the piston in one of the chambers, an air port communicating with the inner end of said chamher, through which pressure on the inner surface of said piston can be controlled, there being an intake port,a.n exhaust port and a brake chamber port in the valve body communicating with the outer end of the other of said piston cham-f bers, an inwardly seating valve controlling said intake port, an outwardly seating valve controlling said exhaust port, a pair of compression springs in the last mentioned chamber acting to seat said valves, the spring that seats the inwardly seating intake port 'valve being arranged to act on the piston in the valved chamber to move it toward the outer end of its stroke, and the spring that seats the outwardly seating exhaust port valve being arranged to act on said piston to move it toward the inner end of its stroke, whereby the pistons normally take an intermediate neutral position, and means moving with the piston in the valved piston chamber adapted to open the intake port valve and allow the exhaust port valve to close as said piston moves to the outer end of its stroke and adapted to allow said intake port valve to close and to open the exhaust portvalve as it moves to the inner end of its stroke.

18. A remote control valve for a fluid pressure brake system, comprising a valve body .having two piston chambers, one of larger diameter than the other, a pair of mechanically connected pistons, one working in each of said chambers, means for applying a pressure on the outer end of the piston in the larger diameter piston chamber, an air port communicating with theinner end of said chamber, through which pressure on the inner surface of said piston can be controlled, there being an intake port, an exhaust port and a brake chamber port in the valve body communicating with the outer end of the other of said piston chambers, an inwardly seating valve controlling said intake port, an outwardly seating valve controlling said exhaust port, a pair of compression springs inthe last mentioned chamber acting to seat said valves, the spring that seats the inwardly seating intake port valve being ber to move it toward the outer end of its stroke, and the spring that seats the outwardly seating exhaust port valve being arranged to act on said piston to move it toward the inner end of its stroke, whereby the pistons normally take an intermediate neutral position, and means moving with the piston in the valve piston chamber adapted to open the intake port valve and allow the exhaust port valve to close as said piston moves to the outer end of its stroke and adapted to allow said intake port valve to close and to open the exhaust port valve as it moves to the inner end of its stroke.

19. A remote control valve for a fluid pressure brake system, comprising a valve body having two piston chambers separated by an intermediate partition, one ofsaid chambers being of larger diameter than the other, a pair of mechanically interconnected pistons, one working in each of said chambers, there being an air port opening into the larger diameter piston chamber through which the pressure on the inner surface 01 the piston in said chamber can be controlled, and an air port in the outer end of said chamber through which pressure air may be introduced to act on the outer surface of said piston, there being an intake port and an exhaust port in the valve body at the outer end of the other piston chamber, an outwardly seating exhaust valve controlling the exhaust port, an inwardly seating intake valve controlling the intake port, a compression spring acting outwardly on the outwardly seating exhaust valve and inwardly on the piston in the valved piston chamber, a compression spring acting inwardly on the inwardly seating intake valve and outwardly on the piston in the valved piston chamber, whereby said pistons normally take an intermediate neutral position in which both said valves are held seated by said springs, and valve actuating means moving with the piston in the valved piston chamber adapted to unseat said intake valve against its arranged to act on the piston in the valved chamspring when said piston moves to the outer end ,valve body at the outer end of one of said chambers, an outwardly seating exhaust valve controlling the exhaust port, an inwardly seating intake valve controlling the intake port, inwardly extending valve stems on said valves, a valve actuating abutment on the piston in the valved piston chamber spaced outwardly from-the outer end of said piston, a compression spring acting outwardly on the stem of the exhaust valve and inwardly onthe abutment carrying piston, a compression spring acting inwardly on the stem of the intake valve and outwardly on said valve actuating abutment, said intake valve stem having a shoulder adapted to be engaged by said abutment to unseat the intake-valve when the abutment carrying piston moves to the outer end of its stroke, said exhaust valve stem having a shoulder adaptedto be engaged by said abutment to unseat the exhaust valve when said piston moves to the inner end of its stroke, there being a brake chamber port in the valve body opening into the outer end of the valved piston chamber, a control: pressure port opening into the inner end of the other piston chamber, and a constant pressure port opening into the outer end of the last mentioned piston chamber.

21. A remote control valve for a fluid pressure brake system, comprising a valve body having two piston chambers separated by an intermediate partition, a pair of mechanically interconnected pistons, one working in each of said chambers,

there being an intake port and an exhaust port in the valve body at the outer end of one of said chambers, an outwardly seating exhaust valve controlling the exhaust port, an inwardly seating intake valve controlling the intake port, inwardly extending valve stems on said valves, a valve actuating abutment on the piston in the valved piston chamber spaced outwardly from the outer end of said piston, a flange on each of said valve stems near the inner ends thereof, a compression spring encircling the intake valve stem and acting inwardly against the" flange on said stem and outwardly against the valve actuating abutment, a compression spring acting outwardly on the exhaust valve stem flange and inwardly on the piston in the adiacent'piston, said intake valve stem having a shoulder adapted to be engaged by said abutment to unseat the intake valve when the abutment carrying-piston moves to the outer end of its stroke, said exhaust valve stem having a shoulder adapted to-beengaged by said abutment to unseat the exhaust valve when said piston moves to the inner end of its, stroke, there partition, a pair of mechanically interconnected pistons, one working in each of said chambers, substantially constant spring means acting to move said pistons toward an intermediate position in their respective chambers, means for applying a pressure on the outer end of the piston in one of the chambers, an air port communicating with the inner end of said chamber, through which pressure on the inner surface of said piston can be controlled, there being an intake port, an exhaust port and a brake chamber port inthe valve body communicating with the outer end of the other of said piston chambers, and a pair of normally closed valves controlling said intake and exhaust ports, the valve controlling the intake port being opened by virtue of movement of the piston in the valved piston chamber from said intermediate position to a position in the direction of the outer end of its stroke and the valve controlling the exhaust port being opened by virtue of moV'ement of the piston from said intermediate position to a position in the direction of the inner end of its stroke.

23. A remote control valve for a fluid pressure brake system, comprising a valve body having piston chambers separated by an intermediate partition, a pair of mechanically interconnected pistons, one working in each of said chambers, substantially constant means for applying a pressure on the outer end of the piston in one of the chambers, an air port communicatingwith the inner end of said chamber, through which pres- ,sure on the inner surface of said piston can be controlled, there being an intake port, an exhaust port and a brake chamber port in the valve body communicating with the outer end of the other of said piston chambers, an inwardly seating valve controlling said intake port, an outwardly seating valve controlling said exhaust port, a pair of compression springs in the last mentioned chamber acting to seat said valves, the spring that seats the inwardly seating intake port valve being arranged to act on the piston in the valved chamber to move it toward the outer end of its stroke, and the spring that seats the outwardly seating exhaust port valve being arranged to act on said piston to move it toward the inner end of its stroke, whereby the pistons normally take an intermediate neutral position, and means moving with-the piston in the valve piston chamber adapted to open the intake port valve and allow the exhaust port valve to close as said piston moves to the outer end of its stroke and adapted to allow said intake port valve to close and to open the exhaust port valveas it moves to the inner end of its stroke.

24. A remote control valve for a fluid pressure brake system, comprising a valve body having two piston chambers, one of larger diameter than the other, a pair of mechanically connected pistons, one working in each of said chambers,

means for applying a substantially constant pressure on the outer end of the piston in the larger diameter piston chamber, an air port communicating with the inner end of said chamber, through which pressure on the inner surface of said piston can be controlled, there being an intake port, an exhaust port and a brake chamber port in the valve body communicating with the outer end of the other of said piston chambers,

an inwardly seating valve controlling said intake port, an outwardly seating valve controlling said, exhaust port, a pair of compression springs in the last mentioned chamber acting to seat said valves the spring that seats the inwardly seating intake port valve being arranged to act on the piston in the valved chamber to move it toward the. outer end of its stroke, and the spring that seats the outwardly seating exhaust port valve being arranged to act on said piston to move it toward the inner end of its stroke, whereby the pistons normally take an intermediate neutral position, and means moving with the piston in the valved piston chamber adapted to open the intake port valve and allow the exhaust port valve to close as said piston moves to the outer end of its stroke and adapted. to allow said intake port valve to close and 'to open the exhaust port valve as it moves to the inner end ofits stroke. I

25. In a fluid pressure brake system, the combination with a supply of pressure fluid and a brake chamber, of a control pressure system, means for controllably supplying said system with fluid from the pressure fluid supply, and for controllably exhausting fluid from said system, and brake pressure control means constantly biased to move in a first direction and directly subject to control system and to brake chamber pressure both applied thereagainst to ,tend to move said means, in a second direction, resilient means yieldingly opposing displacement of said control means in both directions of travel from a neutral position intermediate the two limits of its travel, said control means being ope'ratively responsive to decrease in 'pressurein the control systemto move from said neutral position in said first direction to a position in which pressure fluid is passed from the pressure supply to the brake chamber, and to resulting increase in brake chamberpressure to return to neutral position to interrupt such flow 0i fluid to the brake chamber when brake chamber pressure has risen suiflciently to make up for decreased control system pressure on the control means, said control means also being operatively responsive to subsequent increase in pressure in the control system to move from neutral position in said second direction to a position in which fluid is discharged from the brake chamber, and to resulting decrease in brake chamber fluid pressure to return to neutral position to interrupt discharge of fluid from the brake chamber when brake chamber pressure has decreased sufliciently to compensate for the effected increase oi! control system pressure on-the control means.

26. In a fluid pressure brake system, the combination with a supply of pressure fluid and a brake chamber, of a control pressure system, means for controllably supplying said system with fluid from the pressure fluid supply, and for controllably exhausting fluid from said system, piston means pressure actuated to move in one direction, means applying fluid from the con-' trol system to act on said piston to tend to move it in the opposite direction, spring means yieldingly acting in opposite directions on said piston means to tend to return said piston means toward an intermediate normal position when displaced therefrom in either direction of its travel, said pressure-actuated piston means heing actuated to move in said one direction from said normal position when the control pressure is decreased, means subjecting said piston means 'to' brake chamber fluid pressure, in such direction as to tend to move the piston means in said opposite direction, means supplying pressure fluid to the brake chamber from the pressure fluid supply, normally closed valve means controlling' said means and adapted to be opened by the piston means at a given point in said travel of said piston means in said one direction, discharge means for passing brake chamber pressure fluid to atmosphere, and normally closed valve means controlling said discharge means and adapted to beopened by the piston means at a point in the travel of said piston means in said opposite direction located at a given distance beyond the point of closure of said first mentioned valve means, whereby the piston means has a latitude of travel in the vicinity of said neutral position between the two points at which said two valve means are opened thereby.

27. In a fluid pressure brake system, the combination with a supply of pressure fluid and a brake chamber, of a control pressure system, means for controllably supplying said system with fluid from the pressure fluid supply, and for controllably exhausting fluid from said system, a reciprocable piston means having a fluid pressure area, means applying fluid from the supply of pressure fluid against said piston area to move the piston means in one direction, a fluid pressure area on the piston means facing oppositely to the first named pressure area, means applying fluid from the control system to act on said last named pressure area to tend to move the piston means in the opposite direction, yielding means acting in opposite directions on said piston means to tend to return said piston means toward an intermediate neutral position when displaced therefrom in either direction oi. its travel, said piston means being pressure actuated to move in said one direction when the control pressure isdecreased, another fluid pressure area on said piston means, racing in the same direction as the second named pressure area, means subjecting said last named piston area to brake chamber fluid pressure, means supplying pressure fluid to the brake chamber from the pressure fluid supply, normally closed valve means controlling said means and adapted to be opened by the piston means at a given point in said traveloi'said piston means in said one di-' tion located a given distance beyond the point of closure 01 said first mentioned valve means, whereby the piston means has a latitude of travel in the vicinity of said neutral position between the two points at which said two valve means are opened thereby.

28. In a fluid pressure brake system, the combination with a supply of pressure fluid and a. brake chamber, oi. a control pressure system, means for controllably supplying said system with fluid from the pressure fluid supply, and for controllably exhausting fluid from said system, a reciprocable piston means having a fluid pressure area; means applying fluid from the supply of pressure fluid against said piston area to move the piston means in one, direction, a fluid pressure area on the piston means facing oppositely to the first named pressure area, means applying fluid from the control system to act on said last named pressure area to tend to move the piston meansin the opposite direction, said sition under the "influence of full control system the pressure fluid supply, normally closed valve,

means controlling said means and adapted to be opened by the piston means when said piston means travels from said intermediate position in said one direction, discharge means for passing brake chamber pressure fluid to atmosphere, and normally closed valve means controlling said discharge means and adapted to be opened by the piston means when said piston means travels in said other direction from said intermediate normal position. 29. A remote control'valve for a fluid pressurebrake system, comprising a valve body having piston chambers, a piston means reciprocable therein, said piston means having one fluid pressure area facing in one direction and two fluid pressure areas facing in the opposite direction, three fluid ports opening into the piston chamber that contains one of the two fluid pressure piston areas that face in the same direction, two of said ports normally being closed, one of the latter being opened by the piston means when moved a given distance in one direction from an intermediate position of its stroke, and the other of the two normally closed ports being opened by the piston means when moved a given distance in the other direction from said intermediate placement of said piston means in both directions from said intermediate position and acting to restrain overtravel of said piston means after returning to said intermediate position, and ports through which fluid pressures may be applied to the other two pressure areas on the piston means.

30. In a fluid pressure brake system, the combination with a supply of pressure fluid and a brake chamber, of a piston chamber, three fluid ports opening within said chamber, a fluid conduit between one of the ports andthe pressure fluid supply, a fluid conduit between another of the ports and the brake chamber, and a conduit discharging to atmosphere from the other of the ports, piston and fluid port controlling means in said chamber adapted to open the port connected with the pressure fluid supply when at one position in the chamber, to close said port and open the port discharging to atmosphere when at another position in the chamber, and to close both the last mentioned port and the port connected to the pressure fluid supply when in an intermediate position in the chamber, resilient means yieldingly opposing displacement of said piston means in both directions of travel from said intermediate position, control means comprising a second chamber and piston means, an operative interconnection between the first and second piston means, means applying a force tending to move the two operatively interconnected piston means in such directions as to cause the fluid port. connected to the pressure fluid supply tobe opened, and means controllably supplying pressure fluid from the pressure fluid supply to the second piston means in such direction as to oppose such movement of the two piston means, and forcontrollably releasing said pressure fluid so acting on the second piston means.

AVAD L. FARMER. 

